WO2012039282A1 - 転がり軸受 - Google Patents

転がり軸受 Download PDF

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Publication number
WO2012039282A1
WO2012039282A1 PCT/JP2011/070337 JP2011070337W WO2012039282A1 WO 2012039282 A1 WO2012039282 A1 WO 2012039282A1 JP 2011070337 W JP2011070337 W JP 2011070337W WO 2012039282 A1 WO2012039282 A1 WO 2012039282A1
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WO
WIPO (PCT)
Prior art keywords
diameter side
convex portion
side convex
outer diameter
inner diameter
Prior art date
Application number
PCT/JP2011/070337
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
朋久 魚住
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to US13/818,722 priority Critical patent/US8939649B2/en
Priority to EP11826728.5A priority patent/EP2620663B1/en
Priority to CN201180044987.1A priority patent/CN103109100B/zh
Publication of WO2012039282A1 publication Critical patent/WO2012039282A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3887—Details of individual pockets, e.g. shape or ball retaining means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3862—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together
    • F16C33/3875—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages comprising two annular parts joined together made from plastic, e.g. two injection moulded parts joined by a snap fit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6674—Details of supply of the liquid to the bearing, e.g. passages or nozzles related to the amount supplied, e.g. gaps to restrict flow of the liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7893—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a cage or integral therewith
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2208/00—Plastics; Synthetic resins, e.g. rubbers
    • F16C2208/20—Thermoplastic resins
    • F16C2208/52—Polyphenylene sulphide [PPS]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/70—Positive connections with complementary interlocking parts
    • F16C2226/74—Positive connections with complementary interlocking parts with snap-fit, e.g. by clips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/30—Angles, e.g. inclinations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/60—Thickness, e.g. thickness of coatings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Definitions

  • the present invention relates to a rolling bearing in which a synthetic resin cage that holds a rolling element so as to roll freely is incorporated between an inner ring and an outer ring.
  • various rolling bearings such as deep groove ball bearings and angular ball bearings are widely used for gear support shafts of transmissions of vehicles having motors.
  • This type of ball bearing includes an inner ring having an inner race surface formed on the outer diameter surface, an outer ring disposed on the outer side of the inner ring and having an outer race surface formed on the inner diameter surface, and an inner race surface of the inner ring.
  • a plurality of balls interposed between the outer ring and the outer raceway surface of the outer ring, and a cage that is arranged between the inner ring and the outer ring and holds the balls at equal intervals in the circumferential direction.
  • Either the inner ring or the outer ring is mounted on a fixed part such as a housing, and the other is mounted on a rotating part such as a rotating shaft.
  • the bearing device disclosed in Patent Document 1 is such that a disc-shaped labyrinth forming member is in pressure contact with a small-diameter side end surface of an inner ring facing a flange portion formed radially inward on the small-diameter end side of a cage
  • the labyrinth structure is comprised between the collar part on the small diameter end side of the cage and the labyrinth forming member.
  • the rolling bearing disclosed in Patent Document 2 has a slight guide gap between the inner and outer rings and the cage, the lubricant inflow side end surface of the cage is an inclined surface, and the inner diameter surface of the cage Has an inclined surface.
  • a slight guide clearance is provided between the inner and outer rings and the cage, and the lubricant inflow side end surface of the cage is inclined to suppress excessive drawing of the lubricating oil into the bearing. .
  • the inner diameter surface of the cage an inclined surface, the lubricating oil excessively flowing into the bearing is positively discharged to the outside of the bearing.
  • a labyrinth forming member for forming a labyrinth structure with the flange portion of the cage is required separately from the bearing component, and the inner ring is formed in a small space in the device. It must be attached to the end face on the small diameter side in pressure contact. As a result, the number of parts increases, and it is very difficult to assemble the labyrinth forming member. Therefore, there is a problem that it is difficult to downsize and reduce the number of parts and assembly man-hours.
  • the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to reduce the cost without increasing the number of parts and the number of assembling steps, and the lubricating oil excessively flows into the bearing.
  • An object of the present invention is to provide a rolling bearing capable of reliably suppressing the operation.
  • the present invention is arranged between an inner ring and an outer ring that rotate relative to each other, a plurality of rolling elements interposed between the inner ring and the outer ring, and an inner ring and an outer ring.
  • a retainer that holds the rolling elements at equal intervals in the circumferential direction, and the retainer has a plurality of circumferential hemispherical pockets that accommodate the rolling elements on opposite surfaces of the two annular members facing in the axial direction.
  • a rolling bearing formed at a location and having two opposed annular bodies joined to each other and extending radially to at least one of the inner diameter side and the outer diameter side of the axial end of the annular body
  • a groove corresponding to the flange portion is provided in a portion corresponding to the flange portion of the inner ring or the outer ring.
  • a collar portion extending in the radial direction is provided on at least one of the inner diameter side and the outer diameter side of the axial end portion of the annular body, and the labyrinth is formed at a portion corresponding to the collar portion of the inner ring or outer ring.
  • the cage has an axially symmetrical shape in which a flange is provided at the axial end of the annular body, when the centrifugal force is applied under high-speed rotation, the two annular bodies constituting the cage It is possible to prevent the rolling elements from falling out of the pockets and interfering with other parts such as inner and outer rings by suppressing the deformation of the cages. Furthermore, since the labyrinth is formed by the flange part integrally provided on the annular body and the concave groove formed integrally on the inner and outer rings, it is only necessary to change the shape of the cage and the inner and outer rings. In addition, the number of assembly steps can be reduced and the cost can be reduced easily.
  • the axial thickness of the buttocks is 0.15 mm or more and 20% or less of the diameter of the rolling element.
  • the strength of the collar portion can be secured, the molding of the collar portion is facilitated, and the axial dimension of the bearing is not increased.
  • the axial thickness of the collar portion is smaller than 0.15 mm, insufficient strength or molding failure of the collar portion is likely to occur, and when it is larger than 20% of the diameter of the rolling element, the axial dimension of the cage is reduced.
  • the axial dimensions of the inner and outer rings increase and the size of the bearing increases.
  • the flange portion in the present invention may have either a shape extending in a direction orthogonal to the axial direction or a shape extending in a direction inclined with respect to a direction orthogonal to the axial direction. Regardless of the shape of the flange, it is possible to form a labyrinth with the concave grooves of the inner and outer rings.
  • the inclination direction when inclining a collar part with respect to the direction orthogonal to an axial direction, the inclination direction may be either an axial direction outer side or an axial direction inner side.
  • the cage according to the present invention is configured such that an outer diameter side convex portion is formed by extending an outer diameter side of a circumferential end of one annular body in the axial direction so that an inner circumferential surface thereof can be brought into contact with a rolling element.
  • the inner diameter side is recessed to form an inner diameter side recess
  • the inner circumferential surface of the other annular body pocket is extended in the axial direction to form the inner diameter side convex portion.
  • the outer diameter side convex portion and the inner diameter side convex portion are engaged in the axial direction, and the engagement surface of the outer diameter side convex portion and the inner diameter side convex portion is used as the base end of the outer diameter side convex portion and the inner diameter side convex portion.
  • a structure that is inclined with respect to the axial direction so that the tip side is thicker than the side is desirable.
  • High rotation speed is achieved by a synergistic effect of the frictional force generated along the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion and the axial component of the reaction force generated in the normal direction of the engagement surface. Even when a larger centrifugal force is applied, it is possible to reliably prevent the two annular bodies from separating in the axial direction.
  • the inclination angle of the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion is 5 ° or more.
  • the inner diameter convex portion is thicker than the outer diameter convex portion.
  • the inner diameter side convex portion made thicker than the outer diameter side convex portion is larger in mass than the outer diameter side convex portion.
  • the engagement surface of the outer diameter side convex portion and the inner diameter side convex portion is inclined with respect to the axial direction so that the distal end side is thicker than the proximal end side of the outer diameter side convex portion and the inner diameter side convex portion. Therefore, the deformation of the inner diameter side convex portion acts to increase the coupling force on the engagement surface between the outer diameter side convex portion and the inner diameter side convex portion.
  • a structure in which an outer diameter side convex portion and an inner diameter side concave portion are formed at one circumferential end portion of the pocket and an inner diameter side convex portion and an outer diameter side concave portion are formed at the other circumferential end portion is desirable.
  • the annular body in the present invention is made of a synthetic resin in that the weight of the cage can be reduced.
  • this annular body is preferably molded from any one synthetic resin selected from PPS, PA66, and PA46.
  • a flange extending in the radial direction is provided on at least one of the inner diameter side and the outer diameter side of the axial end portion of the annular body, and the collar portion is provided at a portion corresponding to the flange portion of the inner ring or the outer ring.
  • the cage has an axially symmetrical shape in which a flange is provided at the axial end of the annular body, when the centrifugal force is applied under high-speed rotation, the two annular bodies constituting the cage It is possible to prevent the rolling elements from falling out of the pockets and interfering with other parts such as inner and outer rings by suppressing the deformation of the cages. Furthermore, since the labyrinth is formed by the flange part integrally provided on the annular body and the concave groove formed integrally on the inner and outer rings, it is only necessary to change the shape of the cage and the inner and outer rings. In addition, the number of assembly steps can be reduced and the cost can be reduced easily. As a result, it is possible to provide a rolling bearing for automobiles suitable for a high rotation bearing used in electric vehicles and hybrid vehicles.
  • FIG. 3 is an enlarged cross-sectional view showing a main part of a ball bearing in an embodiment of a rolling bearing according to the present invention. It is an assembly exploded perspective view which shows the two annular bodies which comprise the holder
  • FIG. 3 is an assembled perspective view showing two annular bodies constituting the cage of FIG. 1. It is a partial expanded view which shows the two annular bodies before a coupling
  • FIG. 5 is a cross-sectional view taken along line AA in FIG. 4.
  • FIG. 5 is a sectional view taken along line BB in FIG. 4. It is a partial expanded view which shows the two annular bodies after a coupling
  • FIG. 8 is a cross-sectional view taken along the line CC of FIG.
  • FIG. 8 is a cross-sectional view taken along line DD in FIG. 7. It is principal part expanded sectional drawing which shows the ball bearing in other embodiment of this invention. It is principal part expanded sectional drawing which shows the ball bearing in other embodiment of
  • a ball bearing will be described in detail below as an embodiment of the rolling bearing according to the present invention.
  • the ball bearing of this embodiment is particularly suitable for a high rotation bearing for automobiles used under oil bath lubrication in an electric vehicle or a hybrid vehicle.
  • the ball bearing 1 of this embodiment includes an inner ring 2 having an inner raceway surface 2a formed on the outer diameter surface, and an outer raceway surface 3a on the inner diameter surface.
  • the ball 4 as a plurality of rolling elements interposed between the inner raceway surface 2a of the inner race 2 and the outer raceway surface 3a of the outer race 3, the inner race 2 and the outer race. 3 and the cage 5 that holds the balls 4 at equal intervals in the circumferential direction.
  • Either the inner ring 2 or the outer ring 3 is attached to a fixed part such as a housing, and the other is attached to a rotating part such as a rotating shaft.
  • the ball bearing 1 includes a lightweight synthetic resin cage 5 for the purpose of suppressing deformation of the cage 5 due to centrifugal force under high-speed rotation.
  • this type of cage 5 surrounds a hemispherical pocket 12 that accommodates a ball 4 (see FIG. 1) on opposing surfaces 11 of two annular members 10 facing in the axial direction. It is formed at a plurality of locations in the direction, and has a symmetrical shape in which the opposing surfaces 11 of the annular body 10 are abutted to join the two annular bodies 10 together.
  • the two annular bodies 10 further reduce the weight of the cage 5 by forming a concave thinned portion 17 at a portion between adjacent pockets 12. 2 shows a state before the two annular bodies 10 are joined, and FIG. 3 shows a state after the two annular bodies 10 are joined.
  • the ball bearing 1 of this embodiment has the following structure as a means for restricting the inflow of lubricant into the bearing. That is, the flange 18 extending in the radial direction is provided on the inner diameter side and the outer diameter side of the axial end portion of the annular body 10 (see FIGS. 2 and 3), and corresponds to the flange 18 of the inner ring 2 and the outer ring 3. Concave grooves 20 and 21 in which a labyrinth 19 is formed with the flange 18 are formed in the part (see FIG. 1).
  • the above-described collar portion 18 is formed so as to extend in a direction orthogonal to the axial direction.
  • the groove 20 on the inner ring side is formed so as to dent the outer diameter axial end of the inner ring 2 in a stepped manner, and the groove 21 on the outer ring side forms a stepped shape on the inner ring axial end of the outer ring 3. It is formed so as to be recessed.
  • the collar part 18 of the retainer 5 and the concave grooves 20 and 21 of the inner and outer rings 2 and 3 are not in a positional relationship that is always in contact. That is, the positional relationship between the flange 18 and the grooves 20 and 21 is in contact only under specific conditions or completely non-contact.
  • the labyrinth 19 constituted by the flange portion 18 of the cage 5 and the concave grooves 20 and 21 of the inner and outer rings 2 and 3 reliably suppresses excessive flow of lubricating oil into the bearing.
  • the cage 5 since the cage 5 has an axially symmetrical shape in which the flange portion 18 is provided at the axial end of the annular body 10, the cage 5 is configured when the centrifugal force is applied under high-speed rotation.
  • the annular members 10 can suppress the deformation of the retainers 5 by suppressing the deformation of the retainer 5 so that the balls 4 fall off from the pocket 12 or interfere with other parts such as the inner and outer rings 2 and 3. Can be avoided.
  • the labyrinth 19 is formed by the flange portion 18 provided integrally with the annular body 10 and the concave grooves 20, 21 formed integrally with the inner and outer rings 2, 3, the cage 5 and the inner and outer rings Since only a few shape changes are required, the number of parts and the number of assembling steps can be reduced, and the cost can be easily reduced.
  • the axial thickness t of the flange 18 is set to 0.15 mm or more and 20% or less of the diameter D of the ball 4. As described above, if the axial thickness t of the flange portion 18 is regulated within the above-described range, the strength of the flange portion 18 can be secured, the forming of the flange portion 18 is facilitated, and the axial dimension of the bearing is not increased. . In addition, when the axial direction thickness t of the collar part 18 is smaller than 0.15 mm, the strength of the collar part 18 and insufficient molding are likely to occur.
  • the inner and outer rings 2 and 3 are recessed to prevent the flange 18 of the cage 5 from protruding from the bearing end surface.
  • the axial dimensions (groove width) of the grooves 20 and 21 must be increased, and the axial dimensions of the inner and outer rings 2 and 3 are increased, thereby increasing the size of the entire bearing.
  • the cage 5 of this embodiment includes the following coupling structure as means for coupling the two annular bodies 10 described above.
  • each of the two annular bodies 10 has an outer diameter side convex portion 13 formed by extending the outer diameter side of one circumferential end portion of the pocket 12 in the axial direction and the inner diameter side. Is formed by extending the inner diameter side of the other circumferential end of the pocket 12 in the axial direction to form the inner diameter side convex portion 15 and the outer diameter side is recessed. An outer diameter side recess 16 is formed.
  • the two annular bodies 10 each form the outer diameter side convex portion 13 and the inner diameter side concave portion 14 at one circumferential end portion of the pocket 12, and the inner circumferential side convex portion at the other circumferential end portion.
  • one annular body 10 and the other annular body 10 can be formed by using a kind of annular body 10 manufactured by one mold. The product cost can be reduced.
  • the outer diameter side convex portion 13 of one annular body 10 is inserted into the outer diameter side concave portion 16 of the other annular body 10, and the inner diameter side convex portion 15 of one annular body 10 is inserted into the other annular body 10.
  • the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are engaged in the axial direction.
  • the engagement surfaces 13a, 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are thicker at the distal end side than the proximal end sides of the outer diameter side convex portion 13 and the inner diameter side convex portion 15. It is inclined with respect to the axial direction (see FIGS. 5 and 6).
  • FIG. 7 shows the two annular bodies 10 after joining
  • FIG. 8 is a cross section taken along the line CC in FIG. 7
  • FIG. 9 is a cross section taken along the line DD in FIG.
  • the opposing surfaces 11 of the two annular bodies 10 are brought into contact with each other, and the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are engaged in the axial direction with a predetermined tightening margin.
  • a frictional force is generated along the engagement surfaces 13a, 15a between the outer diameter side convex portion 13 and the inner diameter side convex portion 15.
  • the engagement surfaces 13a, 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are thicker at the distal end side than the proximal end sides of the outer diameter side convex portion 13 and the inner diameter side convex portion 15.
  • the inclination angle ⁇ (see FIGS. 3 and 4) of the engagement surfaces 13a, 15a between the outer diameter side convex portion 13 and the inner diameter side convex portion 15 needs to be 5 ° or more.
  • the inclination angle ⁇ it becomes easy to suppress deformation of the engagement surfaces 13a and 15a when a large centrifugal force is applied due to high rotation, and a reaction force is applied to the engagement surfaces 13a and 15a.
  • An axial component can be made to act reliably, and it becomes easy to ensure the coupling force of the two annular bodies 10.
  • the inclination angle ⁇ of the engagement surfaces 13a and 15a is smaller than 5 °, it becomes difficult to suppress deformation of the engagement surfaces 13a and 15a when a large centrifugal force is applied due to high rotation. It becomes difficult to reliably apply the axial component of the reaction force to the surfaces 13a and 15a.
  • the inner diameter side convex portion 15 is thicker than the outer diameter side convex portion 13 (t IN > t OUT ).
  • the inner diameter side convex portion 15 thicker than the outer diameter side convex portion 13 in this way, the inner diameter side made thicker than the outer diameter side convex portion 13 when a large centrifugal force is applied due to high rotation. Since the mass of the convex portion 15 is larger than that of the outer diameter side convex portion 13, the inner diameter side convex portion 15 is deformed larger than the outer diameter side convex portion 13.
  • the engagement surfaces 13a and 15a of the outer diameter side convex portion 13 and the inner diameter side convex portion 15 are thicker on the distal end side than the proximal end sides of the outer diameter side convex portion 13 and the inner diameter side convex portion 15. Therefore, the deformation of the inner diameter side convex portion 15 increases the coupling force between the outer diameter side convex portion 13 and the inner diameter side convex portion 15 at the engagement surfaces 13a, 15a.
  • the two annular bodies 10 described above are made of synthetic resin in that the weight of the cage 5 can be reduced.
  • it is effective to mold with any one synthetic resin selected from PPS (polyphenylene sulfide), PA66 (polyamide 66) or PA46 (polyamide 46).
  • PPS polyphenylene sulfide
  • PA66 polyamide 66
  • PA46 polyamide 46
  • PA9T polyamide 9T
  • PAEEK polyether ether ketone
  • phenol resin phenol resin
  • the flange portion 18 is formed so as to extend in a direction orthogonal to the axial direction, but the present invention is not limited to this, and the flange portion is orthogonal to the axial direction. You may form so that it may extend in the direction which inclines with respect to the direction to do. In other words, the flange portion 18a may be bent inward in the axial direction as shown in FIG. 10, or the flange portion 18b may be bent outward in the axial direction as shown in FIG. Regardless of the shape of the flanges 18a, 18b, the labyrinth 19 can be formed by the recessed grooves 20, 21 of the inner and outer rings 2, 3.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)
PCT/JP2011/070337 2010-09-22 2011-09-07 転がり軸受 WO2012039282A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US13/818,722 US8939649B2 (en) 2010-09-22 2011-09-07 Rolling bearing
EP11826728.5A EP2620663B1 (en) 2010-09-22 2011-09-07 Rolling bearing
CN201180044987.1A CN103109100B (zh) 2010-09-22 2011-09-07 滚动轴承

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CN108457988A (zh) * 2017-12-30 2018-08-28 广东水利电力职业技术学院（广东省水利电力技工学校） 一种剖分式轴承
CN112112899A (zh) * 2020-08-28 2020-12-22 浙江天马轴承集团有限公司 一种轴承保持架及具有其的轴承
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EP2620663A1 (en) 2013-07-31
CN103109100B (zh) 2016-01-20
US20130156360A1 (en) 2013-06-20
EP2620663B1 (en) 2018-04-25
EP2620663A4 (en) 2017-01-25
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US8939649B2 (en) 2015-01-27
CN103109100A (zh) 2013-05-15

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